TECHNICAL FIELD
[0001] The present invention is suited for application to various screw compressors such
as an injection-type screw compressor for injecting a cooling medium such as oil or
water during compression operation and a dry-type screw compressor which does not
inject anything.
BACKGROUND ART
[0002] Conventionally, a screw compressor disclosed in PTL 1 has been known as an invention
regarding a screw compressor. This screw compressor is configured so that a connector
is provided to connect a rotor casing with a main body casing, an air inlet is located
at a side part of the main body casing, and an intake port is an axial-direction intake
port located at an end of the rotor casing in an axial direction of a screw rotor.
[0003] According to such a configuration, the connector is located in a suction space to
connect the rotor casing with the main body casing. Therefore, it is possible to prevent
heavy vibrations of the rotor casing during the operation of the screw compressor
without significantly increasing manufacturing cost. Specifically speaking, performance
degradation and damage can be prevented by reducing the vibrations of the screw compressor
in operation and it is possible to eliminate the necessity to increase the thickness
of the main body casing as a countermeasure against the vibrations.
[0004] As a result, if the above-described screw compressor is employed, the necessity to
enhance rigidity of the main body casing by adding components can be eliminated. Therefore,
it is possible to reduce the vibrations of the screw compressor in operation and prevent
the performance degradation and the damage without significantly increasing the manufacturing
cost.
CITATION LIST
PATENT LITERATURE
SUMMARY OF THE INVENTION
PROBLEMS TO BE SOLVED BY THE INVENTION
[0006] Screw compressors are in widespread use as air compressors and compressors for refrigeration
and air conditioning. Accordingly, there is a strong demand for energy saving regarding
the screw compressors and it has become increasingly more important to have high energy
efficiency and a large air volume (high capacity). In this case, regarding the injection-type
screw compressor(s), when realizing downsizing to achieve low cost, it is inevitable
to increase a speed for sucking the working medium into a working chamber.
[0007] On the other hand, a dry-type screw compressor(s) cannot expect a sealing effect
by a cooling medium within the working chamber, so that the dry-type screw compressor(s)
is driven at high-speed rotations in excess of 10,000 rotations per minute in order
to reduce leakage loss of the working medium within the working chamber. Specifically
speaking, from the viewpoint of achieving high energy efficiency, as the screw compressor
is driven at higher speeds, the speed of the working medium flowing into the working
chamber will be accelerated quickly. So, the problem is that acceleration loss of
the working medium will increase unless the suction of the working medium into the
working chamber can be performed smoothly.
[0008] The present invention was devised in consideration of the above-described circumstances
and aims at proposing a screw compressor capable of reducing the acceleration loss
of the working medium and compressing the working medium at high energy efficiency.
MEANS TO SOLVE THE PROBLEMS
[0009] In order to solve the above-described problems, there is provided according to the
present invention a screw compressor for compressing a working medium sucked through
a suction opening and discharging the compressed working medium through a delivery
opening, wherein the screw compressor includes: a male rotor and a female rotor that
rotate while meshing with each other; a casing that houses the male rotor and the
female rotor and is provided with a bore which forms a working chamber designed, together
with the male rotor and the female rotor, to compress the working medium; a drive
unit that rotationally drives at least one of the male rotor and the female rotor;
a working chamber closing unit that forms a suction port for sucking the working medium
into the working chamber and closes the working chamber when the working chamber reaches
a specified capacity; and a suction space that connects the suction opening and the
suction port to allow communication therebetween, wherein an open space that connects
the suction opening and the suction port to allow communication therebetween is provided
between a shaft of the male rotor and a shaft of the female rotor on an opposite side
of the male rotor and the female rotor relative to the suction port.
[0010] If the screw compressor according to the present invention is employed, the suction
of the working medium into the working chamber can be performed smoothly with low
flow resistance of the working medium sucked through the suction opening. Accordingly,
when the male rotor and the female rotor rotate at a high speed, the speed will not
be decelerated when the working medium flows into the working chamber. So, energy
efficiency of the screw compressor can be enhanced by suppressing the energy for accelerating
the working medium; and, on the other hand, also when the male rotor and the female
rotor rotate at a low speed, a flow rate of the working medium can be increased along
with a reduction of suction resistance of the working medium.
ADVANTAGEOUS EFFECTS OF THE INVENTION
[0011] The screw compressor capable of reducing the acceleration loss of the working medium
and compressing the working medium at high energy efficiency can be implemented according
to the present invention.
BRIEF DESCRIPTION OF DRAWINGS
[0012]
Fig. 1 is a sectional view illustrating the configuration of a screw compressor according
to a first embodiment;
Fig. 2 is a sectional view illustrating the configuration of the screw compressor
according to the first embodiment (a diagram taken along line A-A indicated with arrows
in Fig. 1);
Fig. 3 is a sectional view illustrating the configuration of the screw compressor
according to the first embodiment (a diagram taken along line B-B indicated with arrows
in Fig. 1);
Fig. 4 is a sectional view illustrating the configuration of the screw compressor
according to the first embodiment (a diagram taken along line C-C indicated with arrows
in Fig. 1);
Fig. 5 is a sectional view illustrating a configuration example of a conventional
screw compressor;
Fig. 6 is a sectional view illustrating the configuration of the conventional screw
compressor corresponding to Fig. 2;
Fig. 7 is a sectional view corresponding to the diagram taken along line C-C indicated
with arrows in Fig. 1 and illustrating the configuration of a screw compressor according
to a second embodiment;
Fig. 8 is a sectional view corresponding to the diagram taken along line C-C indicated
with arrows in Fig. 1 and illustrating the configuration of a screw compressor according
to a third embodiment; and
Fig. 9 is a sectional view corresponding to the diagram taken along line C-C indicated
with arrows in Fig. 1 and illustrating the configuration of a screw compressor according
to a fourth embodiment.
DESCRIPTION OF EMBODIMENTS
[0013] One embodiment of the present invention will be described below in detail with reference
to the drawings.
(1) First Embodiment
[0014] Fig. 1 to Fig. 4 illustrate a screw compressor according to a first embodiment. Fig.
1 is a diagram taken along line D-D indicated with arrows in Fig. 2; Fig. 2 is a diagram
taken along line A-A indicated with arrows in Fig. 1; Fig. 3 is a diagram taken along
line B-B indicated with arrows in Fig. 1 and Fig. 2; and Fig. 4 is a diagram taken
along line C-C indicated with arrows in Fig. 1 and Fig. 2.
[0015] A screw compressor 1 according to this embodiment is configured, as illustrated in
Fig. 1 and Fig. 2, by including a male rotor 2 and a female rotor 3 which are screw
rotors, and a casing 4 for housing the male rotor 2 and the female rotor 3.
[0016] The male rotor 2 is configured by including: a lobe unit 2A provided with a plurality
of (four in this embodiment) spirally extending lobes 2AA (Fig. 3 and Fig. 4); a suction-side
shaft 2B connected to one end side of the lobe unit 2A in its rotor shaft direction
(the left side in Fig. 1 and Fig. 2); and a delivery-side shaft 2C connected to the
other end side of the lobe unit 2A in the rotor shaft direction (the right side in
Fig. 1 and Fig. 2). The suction-side shaft 2B of the male rotor 2 is freely rotatably
supported by a suction-side bearing 5 and the delivery-side shaft 2C of the male rotor
2 is freely rotatably supported by a delivery-side bearing 7.
[0017] Similarly, the female rotor 3 is configured by including: a lobe unit 3A provided
with a plurality of (six in this embodiment) spirally extending lobes 3AA (Fig. 3
and Fig. 4); a suction-side shaft 3B connected to one end side of the lobe unit 3A
in its rotor shaft direction; and a delivery-side shaft 3C connected to the other
end side of the lobe unit 3A in the rotor shaft direction. The suction-side shaft
3B of the female rotor 3 is freely rotatably supported by a suction-side bearing 6
and the delivery-side shaft 3C of the female rotor 3 is freely rotatably supported
by a delivery-side bearing 8.
[0018] The suction-side shaft 2B of the male rotor 2 pierces through the casing 4 and is
coupled to a rotating shaft 9B of a motor 9A which configures a drive unit 9. Accordingly,
the male rotor 2 can be rotationally driven integrally with the rotating shaft 9B
of the motor 9A by driving the motor 9A. Furthermore, the female rotor 3 can be also
rotationally driven integrally with the male rotor 2 by means of meshing between the
lobe unit 2A of the male rotor 2 and the lobe unit 3A of the female rotor 3. However,
either the male rotor 2 or the female rotor 3 may be driven when driving the screw
compressor 1. Moreover, the male rotor 2 and the female rotor 3 may be synchronized
with each other and both of them may be driven by the motor.
[0019] The casing 4 is composed of a main casing 10 and a D casing 11 coupled to the other
end side of the main casing 10 in the rotor shaft direction (the right side in Fig.
1 and Fig. 2). The following are formed in the D casing 11: a delivery opening 11A
positioned outside, in a rotor diameter direction, of the lobe unit 2A of the male
rotor 2 and the lobe unit 3A of the female rotor 3 (the lower side in Fig. 1); and
a delivery passage 11B formed to connect the delivery opening 11A and a working chamber
described later.
[0020] Furthermore, a bore 10A for housing the lobe unit 2A of the male rotor 2 and the
lobe unit 3A of the female rotor 3 is formed in the main casing 10 as illustrated
in Fig. 3. The bore 10A is a space shaped as two cylindrical holes which partially
overlap with each other and are designed to house the lobe unit 2A of the male rotor
2 and the lobe unit 3A of the female rotor 3 in a state where the lobe unit 2A and
the lobe unit 3A mesh with each other.
[0021] An inner wall surface of the bore 10A, a groove 2AB (Fig. 3 and Fig. 4) for the male
rotor 2, and a groove 3AB (Fig. 3 and Fig. 4) for the female rotor 3 form the working
chamber. The working chamber is formed so that its volume gradually decreases from
its one side in the rotor shaft direction (the left side in Fig. 1 and Fig. 2) to
the other side (the right side in Fig. 1 and Fig. 2). Accordingly, a working medium
such as air sucked through the suction opening 12 is gradually compressed in the working
chamber and is then delivered from the delivery opening 11A through the delivery passage
11B.
[0022] The suction opening 12 is formed outside, in the rotor diameter direction, of the
lobe unit 2A of the male rotor 2 and the lobe unit 3A of the female rotor 3 in the
main casing 10 (the upper side in Fig. 1). The suction opening 12 is connected to
a suction port via the suction space 13 to allow communication therebetween as illustrated
in Fig. 1 and Fig. 2 and the working medium sucked through the suction opening 12
sequentially passes through the suction space 13 and the suction port and is then
sucked into the working chamber. Incidentally, the suction port is a port provided
on a plane surface which includes an end face of the one end side of the lobe unit
2A of the male rotor 2 in the rotor shaft direction and an end face of the one end
side of the lobe unit 3A of the female rotor 3 in the rotor shaft direction inside
the bore 10A and which is perpendicular to an axial rection of the male rotor 2 and
the female rotor 3.
[0023] A working chamber closing member 14 of a plate shape is located at the suction port
so as to close the end face of the one end side of the lobe unit 2A of the male rotor
2 and the end face of the one end side of the lobe unit 3A of the female rotor 3 (to
close the working chamber) when the working chamber reaches the maximum capacity.
Practically, the working chamber closing member 14 is located between the suction-side
shaft 2B of the male rotor 2 and the suction-side shaft 3B of the female rotor 3 so
that one surface (hereinafter referred to as a "rotor-facing surface") 14A side opposite
the end face on the one end side of the lobe unit 2A of the male rotor 2 in the rotor
shaft direction and the end face on the one end side of the lobe unit 3A of the female
rotor 3 in the rotor shaft direction will be located on the suction port.
[0024] Furthermore, an arc-shaped depression 14C which is coaxial with the suction-side
shaft 2B (i.e., which is centered at the center of the rotor shaft of the male rotor
2) and has a diameter (radius) larger than that of the suction-side shaft 2B to a
certain degree is formed on the opposite side of the male rotor 2 and the female rotor
3 relative to the suction port and at a position opposite the suction-side shaft 2B
of the male rotor 2 in the working chamber closing member 14. Accordingly, a space
of a certain size (hereinafter referred to as a "male-rotor-side open space") 15A
is formed between the suction-side shaft 2B of the male rotor 2 and the depression
14C of the working chamber closing member 14.
[0025] Similarly, an arc-shaped depression 14D which is coaxial with the suction-side shaft
3B (i.e., which is centered at the center of the rotor shaft of the female rotor 3)
and has a diameter larger than of the suction-side shaft 3B to a certain degree is
formed at a position opposite the suction-side shaft 3B of the female rotor 3 in the
working chamber closing member 14. Accordingly, a space of a certain size (hereinafter
referred to as a "female-rotor-side open space") 15B is formed between the suction-side
shaft 3B of the female rotor 3 and the depression 14D of the working chamber closing
member 14.
[0026] In this case, the diameter of the depression 14C or 14D in the working chamber closing
member 14 is selected to be smaller than a root diameter of the male rotor 2 or the
female rotor 3 and to be larger than a radius of the suction-side shaft 2B of the
male rotor 2 or the suction-side shaft 3B of the female rotor 3 so that the working
chamber can be closed.
[0027] Furthermore, an open space which is positioned between the suction-side shaft 2B
of the male rotor 2 and the suction-side shaft 3B of the female rotor 3 and is connected
to the suction space 13 and both the male-rotor-side open space 15A and the female-rotor-side
open space 15B, respectively, to allow communication therebetween (hereinafter referred
to as a "motor-side open space") 15C is provided on the other surface of the working
chamber closing member 14 on the opposite side of the rotor-facing surface 14A (hereinafter
referred to as an "opposite rotor-facing surface") 14B.
[0028] Incidentally, this motor-side open space 15C and the male-rotor-side open space 15A
and the female-rotor-side open space 15B will be hereinafter collectively referred
to as an open space 15. This open space 15 is a section that connects the suction
space 13 which exists outside the suction-side shaft 2B of the male rotor 2, and the
suction space 13 which exists outside the suction-side shaft 3B of the female rotor
3, to the suction port to allow communication therebetween.
[0029] Now, each of Fig. 5 and Fig. 6 in which the same reference numerals as those used
in Fig. 2 and Fig. 4 are assigned with a prime symbol ("'") attached thereto to parts
corresponding to those in Fig. 2 and Fig. 4 illustrates the structure of the parts
corresponding to Fig. 2 and Fig. 4 in a corresponding screw compressor 1'. As is apparent
from Fig. 5 and Fig. 6, the conventional screw compressor 1' is designed so that:
a space similar to the open space 15C according to this embodiment is not provided
on the opposite side of a rotor-facing surface 16A of a working chamber closing unit
16 corresponding to the working chamber closing member 14 according to this embodiment;
and the working chamber closing unit 16 is formed integrally with a main casing 10'
to fill up the part corresponding to this open space 15C.
[0030] Moreover, with the conventional screw compressor 1', the arc-shaped depression 16B
which is coaxial with a suction-side shaft 2B' is formed at a position opposite the
suction-side shaft 2B' of a male rotor 2' in the working chamber closing unit 16,
but the diameter of this depression 16B is selected to a degree of not impeding rotations
of the suction-side shaft 2B' of the male rotor 2. Accordingly, only a minute clearance
is formed between the working chamber closing unit 16 and the suction-side shaft 2B'
of the male rotor 2' and no space like the male-rotor-side open space 15A (Fig. 4)
of the screw compressor 1 according to this embodiment exists.
[0031] Similarly, with the conventional screw compressor 1', the arc-shaped depression 16C
which is coaxial with a suction-side shaft 3B' is formed at a position opposite the
suction-side shaft 3B of the female rotor 3 in the working chamber closing unit 16,
but the diameter of this depression 16C is selected to a degree of not impeding rotations
of the suction-side shaft 3B' of a female rotor 3'. Accordingly, only a minute clearance
is formed between the working chamber closing unit 16 and the suction-side shaft 3B'
of the female rotor 3' and no space like the female-rotor-side open space 15B (Fig.
4) of the screw compressor 1 according to this embodiment exists.
[0032] Regarding the conventional screw compressor 1' having the above-described configuration,
the working medium sucked through the suction opening passes through respectively
a suction space 13' which exists outside the suction-side shaft 2B' of the male rotor
2', and a suction space 13' which exists outside the suction-side shaft 3B' of the
female rotor 3', and then flows into the screw compressor 1'; and since a flow of
the working medium which flows through these suction spaces 13' is dammed up by the
working chamber closing unit 16, flow resistance within the suction spaces 13' increases,
thereby impeding the suction of the working chamber into the working chamber.
[0033] On the other hand, regarding the screw compressor 1 according to this embodiment,
the working medium sucked through the suction opening 12 passes through respectively
a space part of the suction space 13 which exists outside the suction-side shaft 2B
of the male rotor 2, and a space part of the suction space 13 which exists outside
the suction-side shaft 3B of the female rotor 3, and then flows into the screw compressor
1 in a manner similar to that of the conventional screw compressor 1'. In this case,
the working medium which flows through these respective space parts of the suction
space 13 flows into the open space 15 which is composed of the male-rotor-side open
space 15A, the female-rotor-side open space 15B, and the motor-side open space 15C,
so that the flow of the working medium which passes through the space part of the
suction space existing outside the suction-side shaft 2B of the male rotor 2 and the
space part of the suction space 13 existing outside the suction-side shaft 3B of the
female rotor 3 and then flows into the screw compressor 1 is not dammed up by the
working chamber closing member 14.
[0034] Then, part of the working medium which has flown through the space part of the suction
space 13 existing outside the suction-side shaft 2B of the male rotor 2 collides against
a side wall on the male rotor 2 side of the working chamber closing member 14, then
passes through the male-rotor-side open space 15A between the depression 14C of the
working chamber closing member 14 and the suction-side shaft 2B of the male rotor
2, then flows within the suction space 13 and the open space 15 as if rotating around
the suction-side shaft 2B of the male rotor 2 in the same direction as a rotation
direction of the suction-side shaft 2B (the rotation direction indicated with arrow
a in Fig. 4), and is eventually sucked into the working chamber through the suction
port.
[0035] Furthermore, the remaining working medium collides against the working medium, which
has flown through the space part of the suction space 13 existing outside the suction-side
shaft 3B of the female rotor 3, in the motor-side open space 15C, then flows within
the suction space 13 and the open space 15 as if rotating around the suction-side
shaft 2B of the male rotor 2 in the same direction as the rotation direction of the
suction-side shaft 2B, and is eventually sucked into the working chamber through the
suction port.
[0036] Similarly, part of the working medium which has flown through the space part of the
suction space 13 existing outside the suction-side shaft 3B of the female rotor 3
collides against a side wall on the female rotor 3 side of the working chamber closing
member 14, then passes through the female-rotor-side open space 15B between the depression
14D of the working chamber closing member 14 and the suction-side shaft 3B of the
female rotor 3, then flows within the suction space 13 and the open space 15 as if
rotating around the suction-side shaft 3B of the female rotor 3 in the same direction
as a rotation direction of the suction-side shaft 3B (the rotation direction indicated
with arrow b in Fig. 4), and is eventually sucked into the working chamber through
the suction port.
[0037] Furthermore, the remaining working medium collides against the working medium, which
has flown through the space part of the suction space 13 existing outside the suction-side
shaft 2B of the male rotor 2, in the motor-side open space 15C, then flows within
the suction space 13 and the open space 15 as if rotating around the suction-side
shaft 3B of the female rotor 3 in the same direction as the rotation direction of
the suction-side shaft 3B, and is eventually sucked into the working chamber through
the suction port.
[0038] Therefore, the screw compressor 1 according to this embodiment is provided with the
open space 15 which is composed of the male-rotor-side open space 15A, the female-rotor-side
open space 15B, and the motor-side open space 15C, it has lower flow resistance of
the working medium sucked through the suction opening 12 than that of the conventional
screw compressor 1' and the suction of the working medium into the working chamber
is performed smoothly.
[0039] Accordingly, when the male rotor 2 and the female rotor 3 rotate at a high speed,
the speed is not decelerated when the working medium flows into the working chamber;
and, therefore, energy efficiency of the screw compressor can be enhanced by suppressing
the energy for accelerating the working medium. On the other hand, when the male rotor
2 and the female rotor 3 rotate at a low speed, a flow rate of the working medium
can be increased along with a reduction of suction resistance of the working medium.
Therefore, if this screw compressor 1 is employed, acceleration loss of the working
medium can be reduced and the working medium can be compressed at high energy efficiency.
(2) Second Embodiment
[0040] Fig. 7 in which the same reference numerals as those used in Fig. 4 or such same
reference numerals with suffix "X" added thereto are assigned to parts corresponding
to those in Fig. 4 illustrates a partial configuration of a screw compressor according
to a second embodiment and corresponds to a diagram taken along line C-C indicated
with arrows in Fig. 1. The screw compressor according to this embodiment is configured
in a manner similar to the screw compressor 1 according to the first embodiment, except
that, instead of the working chamber closing member 14 (Fig. 1, Fig. 2, Fig. 4) according
to the first embodiment, a working chamber closing unit 20 of the same size as that
of the working chamber closing unit 16 is formed integrally with a main casing 10X
at the same position as the conventional working chamber closing unit 16 described
earlier with reference to Fig. 6.
[0041] In this case, the working chamber closing unit 20 of the screw compressor according
to this embodiment has a male-rotor-side recess 20A and a female-rotor-side recess
20B which are formed by grinding a side part opposite the male rotor 2 and a side
part opposite the female rotor 3 so that it extends from one end of the motor 9A (Fig.
1) side of the rotor shaft direction and reaches the vicinity of a rotor-facing surface
(a surface opposite an end of the lobe unit 2A of the male rotor 2 and the lobe unit
3A of the female rotor 3). Moreover, the male-rotor-side recess 20A and the female-rotor-side
recess 20B are respectively formed in a curved shape which is smoothly joined to an
inner wall surface of a bore 10AX as viewed from the rotor shaft direction of the
male rotor 2 and the female rotor 3.
[0042] Then, by forming the male-rotor-side recess 20A and the female-rotor-side recess
20B in the working chamber closing unit 20 as described above, a first male-rotor-side
open space 21A of the same shape as that of the male-rotor-side recess 20A is formed
between an isolation wall 20C of the working chamber closing unit 20, which isolates
the male-rotor-side recess 20A from the female-rotor-side recess 20B, and the suction-side
shaft 2B of the male rotor 2 and a first female-rotor-side open space 22A of the same
shape as that of the female-rotor-side recess 20B is formed between the isolation
wall 20 and the suction-side shaft 3B of the female rotor 3.
[0043] Furthermore, an arc-shaped depression 20D which is coaxial with the suction-side
shaft 2B of the male rotor 2 and has a diameter larger than that of the suction-side
shaft 2B to a certain degree is formed in the working chamber closing unit 20 at a
position opposite the suction-side shaft 2B of the male rotor 2 on the rotor-facing
surface side. Accordingly, a second male-rotor-side open space 21B of a certain size
which is connected to the first male-rotor-side open space 21A to allow communication
therewith and configures, together with the first male-rotor-side open space 21A,
a first open space 21 is formed between the suction-side shaft 2B of the male rotor
2 and the working chamber closing unit 20.
[0044] Similarly, an arc-shaped depression 20E which is coaxial with the suction-side shaft
3B of the female rotor 3 and has a diameter larger than that of the suction-side shaft
3B to a certain degree is formed in the working chamber closing unit 20 at a position
opposite the suction-side shaft 3B of the female rotor 3 on the rotor-facing surface
side. Accordingly, a second female-rotor-side open space 22B of a certain size which
is connected to the second female-rotor-side open space 22A to allow communication
therewith and configures, together with the first female-rotor-side open space 22A,
a second open space 22 is formed between the suction-side shaft 3B of the female rotor
3 and the working chamber closing unit 20.
[0045] In this case, the diameter of the depression 20D or 20E of the working chamber closing
unit 20 is selected to be smaller than a root diameter of the male rotor 2 or the
female rotor 3 and to be larger than the radius of the suction-side shaft 2B of the
male rotor 2 or the suction-side shaft 3B of the female rotor 3 so that the working
chamber can be closed.
[0046] With the screw compressor according to this embodiment having the above-described
configuration, the working medium which has flown through the space part of the suction
space 13 (Fig. 1 and Fig. 2) existing outside the suction-side shaft 2B of the male
rotor 2 flows within the suction space 13 and the first open space 21 as if rotating
around the suction-side shaft 2B of the male rotor 2 in the same direction as a rotation
direction of the suction-side shaft 2B (the rotation direction indicated with arrow
a) along a wall surface of the male-rotor-side recess 20A of the working chamber closing
unit 20 and is eventually sucked into the working chamber through the suction port.
[0047] Furthermore, part of the working medium which has flown through the space part of
the suction space 13 existing outside the suction-side shaft 2B of the male rotor
2 collides against a side wall on the rotor-facing surface side of the working chamber
closing member 14, then passes through the second male-rotor-side open space 21B of
the working chamber closing member 20, then flows within the suction space 13 and
the first open space 21 as if rotating around the suction-side shaft 2B of the male
rotor 2 in the same direction as the rotation direction of the suction-side shaft
2B, and is eventually sucked into the working chamber through the suction port.
[0048] Similarly, with this screw compressor, the working medium which has flown through
the space part of the suction space 13 (Fig. 1 and Fig. 2) existing outside the suction-side
shaft 3B of the female rotor 3 flows within the suction space 13 and the second open
space 22 as if rotating around the suction-side shaft 3B of the female rotor 3 in
the same direction as a rotation direction of the suction-side shaft 3B (the rotation
direction indicated with arrow b) along a wall surface of the female-rotor-side recess
20B of the working chamber closing unit 20 and is eventually sucked into the working
chamber through the suction port.
[0049] Furthermore, part of the working medium which has flown through the space part of
the suction space 13 existing outside the suction-side shaft 3B of the female rotor
3 collides against a side wall on the rotor-facing surface side of the working chamber
closing member 20, then passes through the second female-rotor-side open space 22B
of the working chamber closing member 20, then flows within the suction space 13 and
the second open space 22 as if rotating around the suction-side shaft 3B of the female
rotor 3 in the same direction as the rotation direction of the suction-side shaft
3B, and is eventually sucked into the working chamber through the suction port.
[0050] The screw compressor according to this embodiment is configured as described above
so that the first open space 21 and the second open space 22 are separated from each
other; and, therefore, it exhibits the effect of rectifying the working medium which
flows within, for example, the suction space 13 along with the rotations of the male
rotor 2 and the female rotor 3. Particularly, when the male rotor 2 and the female
rotor 3 rotate at a high speed, this rectification effect is valid; and in a case
of the screw compressor with a low low-speed operation ratio, it has a high suction
resistance effect. Moreover, regarding this screw compressor, the male-rotor-side
recess 20A and the female-rotor-side recess 20B of the working chamber closing unit
20 are respectively formed in a curved shape which is smoothly joined to the inner
wall surface of the bore 10AX, so that it exhibits the effect of further impeding
disturbances of the flow of the working medium which flows within, for example, the
suction space 13.
[0051] Therefore, if the screw compressor according to this embodiment is employed, the
working medium sucked through the suction opening 12 (Fig. 1) has lower flow resistance
than that of the conventional screw compressor and the suction of the working medium
into the working chamber is performed smoothly. Accordingly, when the male rotor 2
and the female rotor 3 rotate at a high speed, the speed is not decelerated when the
working medium flows into the working chamber; and, therefore, energy efficiency of
the screw compressor can be enhanced by suppressing the energy for accelerating the
working medium. Also, when the male rotor 2 and the female rotor 3 rotate at a low
speed, the flow rate of the working medium can be increased along with a reduction
of the suction resistance of the working medium.
(3) Third Embodiment
[0052] Fig. 8 in which the same reference numerals as those used in Fig. 4 or such same
reference numerals with suffix "Y" added thereto are assigned to parts corresponding
to those in Fig. 4 illustrates a partial configuration of a screw compressor according
to a third embodiment and corresponds to a diagram taken along line C-C indicated
with arrows in Fig. 1. The screw compressor according to this embodiment is configured
in a manner similar to the screw compressor 1 according to the second embodiment,
except that the configuration of a working chamber closing unit 30 is different.
[0053] Practically, with the screw compressor according to this embodiment, the working
chamber closing unit 30 of the same size as that of the working chamber closing unit
16 is formed integrally with a main casing 10Y at the same position as that of the
conventional working chamber closing unit 16 described earlier with reference to Fig.
6.
[0054] This working chamber closing unit 30 has a male-rotor-side recess 30A and a female-rotor-side
recess 30B which are formed on a side part opposite the male rotor 2 and a side part
opposite the female rotor 3, respectively, so that they extend from an end of the
motor 9A (Fig. 1) side in the rotor shaft direction and reach the vicinity of a rotor-facing
surface (a surface opposite an end of the lobe unit 2A of the male rotor 2 and the
lobe unit 3A of the female rotor 3).
[0055] Then, by forming the male-rotor-side recess 30A and the female-rotor-side recess
30B in the working chamber closing unit 30 as described above, a first male-rotor-side
open space 31A of the same shape as that of the male-rotor-side recess 30A is formed
between an isolation wall 30C of the working chamber closing unit 30, which isolates
the male-rotor-side recess 30A from the female-rotor-side recess 30B, and the suction-side
shaft 2B of the male rotor 2 and a first female-rotor-side open space 32A of the same
shape as that of the female-rotor-side recess 30B is formed between the isolation
wall 30 and the suction-side shaft 3B of the female rotor 3.
[0056] In this case, the male-rotor-side recess 30A is designed with its side face formed
in an arc shape so that its curvature increases from an inlet side of the first male-rotor-side
open space 31A for the working medium, which flows into the first male-rotor-side
open space 31A as described later, towards its outlet side; and, therefore, a curvature
of the first male-rotor-side open space 31A increases towards the rotation direction
of the suction-side shaft 2B of the male rotor 2.
[0057] Similarly, the female-rotor-side recess 30B is designed with its side face formed
in an arc shape so that its curvature increases from an inlet side of the first female-rotor-side
open space 32A for the working medium, which flows into the first female-rotor-side
open space 32A as described later, towards its outlet side; and, therefore, a curvature
of the first female-rotor-side open space 32A increases towards the rotation direction
of the suction-side shaft 3B of the female rotor 3.
[0058] Furthermore, an arc-shaped depression 30D which is coaxial with the suction-side
shaft 2B of the male rotor 2 and has a diameter larger than that of the suction-side
shaft 2B to a certain degree is formed in the working chamber closing unit 30 at a
position opposite the suction-side shaft 2B of the male rotor 2 on the rotor-facing
surface side. Accordingly, a second male-rotor-side open space 31B of a certain size
which is connected to the first male-rotor-side open space 31A to allow communication
therewith and configures, together with the first male-rotor-side open space 31A,
a first open space 31 is formed between the suction-side shaft 2B of the male rotor
2 and the working chamber closing unit 30.
[0059] Similarly, an arc-shaped depression 30E which is coaxial with the suction-side shaft
3B of the female rotor 3 and has a diameter larger than that of the suction-side shaft
3B to a certain degree is formed in the working chamber closing unit 30 at a position
opposite the suction-side shaft 3B of the female rotor 3 on the rotor-facing surface
side. Accordingly, a second female-rotor-side open space 32B of a certain size which
is connected to the second female-rotor-side open space 32A to allow communication
therewith and configures, together with the first female-rotor-side open space 32A,
a second open space 32 is formed between the suction-side shaft 3B of the female rotor
3 and the working chamber closing unit 30.
[0060] Incidentally, the diameter of the depression 30D or 30E of the working chamber closing
unit 30 is selected to be smaller than a root diameter of the male rotor 2 or the
female rotor 3 and to be larger than the radius of the suction-side shaft 2B of the
male rotor 2 or the suction-side shaft 3B of the female rotor 3 so that the working
chamber can be closed.
[0061] With the screw compressor according to this embodiment having the above-described
configuration, the working medium which has flown through the space part of the suction
space 13 (Fig. 1 and Fig. 2) existing outside the suction-side shaft 2B of the male
rotor 2 flows within the suction space 13 and the first open space 21 as if rotating
around the suction-side shaft 2B of the male rotor 2 in the same direction as the
rotation direction of the suction-side shaft 2B (the rotation direction indicated
with arrow a) along a wall surface of the male-rotor-side recess 30A of the working
chamber closing unit 30 and is eventually sucked into the working chamber through
the suction port.
[0062] Furthermore, part of the working medium which has flown through the space part of
the suction space 13 existing outside the suction-side shaft 2B of the male rotor
2 collides against a side wall on the rotor-facing surface side of the working chamber
closing member 30, then passes through the second male-rotor-side open space 31B of
the working chamber closing member 30, then flows within the suction space 13 and
the first male-rotor-side open space 31A as if rotating around the suction-side shaft
2B of the male rotor 2 in the same direction as the rotation direction of the suction-side
shaft 2B, and is eventually sucked into the working chamber through the suction port.
[0063] Similarly, with this screw compressor, the working medium which has flown through
the space part of the suction space 13 (Fig. 1 and Fig. 2) existing outside the suction-side
shaft 3B of the female rotor 3 flows within the suction space 13 and the second open
space 32 as if rotating around the suction-side shaft 3B of the female rotor 3 in
the same direction as the rotation direction of the suction-side shaft 3B (the rotation
direction indicated with arrow b) along a wall surface of the female-rotor-side recess
30B of the working chamber closing unit 30 and is eventually sucked into the working
chamber through the suction port.
[0064] Furthermore, part of the working medium which has flown through the space part of
the suction space 13 existing outside the suction-side shaft 3B of the female rotor
3 collides against a side wall on the rotor-facing surface side of the working chamber
closing member 30, then passes through the second female-rotor-side open space 32B
of the working chamber closing member 30, then flows within the suction space 13 and
the second open space 32 as if rotating around the suction-side shaft 3B of the female
rotor 3 in the same direction as the rotation direction of the suction-side shaft
3B, and is eventually sucked into the working chamber through the suction port.
[0065] The screw compressor according to this embodiment is configured as described above
so that the first open space 31 and the second open space 32 are separated from each
other; and, therefore, it exhibits the effect of rectifying the working medium which
flows within, for example, the suction space 13 along with the rotations of the male
rotor 2 and the female rotor 3 in a manner similar to that of the screw compressor
according to the second embodiment.
[0066] Consequently, if the screw compressor according to this embodiment is employed, the
working medium sucked through the suction opening 12 (Fig. 1) has lower flow resistance
than that of the conventional screw compressor and the suction of the working medium
into the working chamber is performed smoothly in a manner similar to that of the
screw compressor according to the second embodiment. Accordingly, when the male rotor
2 and the female rotor 3 rotate at a high speed, the speed is not decelerated when
the working medium flows into the working chamber; and, therefore, energy efficiency
of the screw compressor can be enhanced by suppressing the energy for accelerating
the working medium. Also, when the male rotor 2 and the female rotor 3 rotate at a
low speed, the flow rate of the working medium can be increased along with a reduction
of the suction resistance of the working medium.
[0067] In addition, with this screw compressor, the first male-rotor-side open space 31A
or the first female-rotor-side open space 32A is formed in an arc shape with a larger
curvature on its outlet side than that on its inlet side, a flow passage area of the
working medium which flows within the first male-rotor-side open space 31A or the
first female-rotor-side open space 31B is narrowed on the outlet side. Accordingly,
the speed of the working medium which flows out of the outlet side of the first male-rotor-side
open space 31A or the first female-rotor-side open space 31B can be increased and
the acceleration loss of the working medium can be reduced.
[0068] Furthermore, with this screw compressor, a side-face shape of the male-rotor-side
recess 30A and a side-face shape of the female-rotor-side recess 30B are formed in
a substantially cylindrical shape, so that processing of the working chamber closing
unit 30 is facilitated, thereby making it possible to improve manufacturing efficiency
of the screw compressor and reduce manufacturing cost.
(4) Fourth Embodiment
[0069] Fig. 9 in which the same reference numerals as those used in Fig. 4 or such same
reference numerals with suffix "Z" added thereto are assigned to parts corresponding
to those in Fig. 4 illustrates a partial configuration of a screw compressor according
to a fourth embodiment and corresponds to a diagram taken along line C-C indicated
with arrows in Fig. 1. The screw compressor according to this embodiment is configured
in a manner similar to the screw compressor according to the third embodiment, except
that the configuration of a working chamber closing unit 40 is different.
[0070] Practically, with the screw compressor according to this embodiment, a working chamber
closing unit 40 with the same length in the rotor shaft direction as that of the working
chamber closing unit 16 is formed integrally with a main casing 10Z at the same position
as that of the conventional working chamber closing unit 16 described earlier with
reference to Fig. 6.
[0071] This working chamber closing unit 40 has a male-rotor-side recess 40A and a female-rotor-side
recess 40B which are formed at a side part on the male rotor 2 side and a side part
on the female rotor 3 side, respectively, so that they extend from an end of the motor
9A (Fig. 1) side in the rotor shaft direction and reach the rotor-facing surface.
[0072] Then, by forming the male-rotor-side recess 40A and the female-rotor-side recess
40B in the working chamber closing unit 40 as described above, a male-rotor-side open
space 41A is formed between the male-rotor-side recess 40A and the suction-side shaft
2B of the male rotor 2 and a female-rotor-side open space 41B is formed between the
female-rotor-side recess 40B and the suction-side shaft 3B of the female rotor 3.
[0073] In this case, the diameter of the male-rotor-side recess 40A or the female-rotor-side
recess 40B of the working chamber closing unit 40 is selected to be smaller than a
root diameter of the male rotor 2 or the female rotor 3 and to be larger than the
radius of the suction-side shaft 2B of the male rotor 2 or the suction-side shaft
3B of the female rotor 3 so that the working chamber can be closed.
[0074] Furthermore, the male-rotor-side recess 40A of the working chamber closing unit 40
is designed with its side face formed in an arc shape so that its curvature increases
from an inlet side of the male-rotor-side open space 41A for the working medium, which
flows into the male-rotor-side open space 41A as described later, towards its outlet
side; and, therefore, a curvature of the male-rotor-side open space 41A increases
towards the rotation direction of the suction-side shaft 2B of the male rotor 2.
[0075] Similarly, the female-rotor-side recess 40B of the working chamber closing unit 40
is designed with its side face formed in an arc shape so that its curvature increases
from an inlet side of the female-rotor-side open space 41B for the working medium,
which flows into the female-rotor-side open space 41B as described later, towards
its outlet side; and, therefore, a curvature of the female-rotor-side open space 41B
increases towards the rotation direction of the suction-side shaft 3B of the female
rotor 3.
[0076] With the screw compressor according to this embodiment having the above-described
configuration, the working medium which has flown through the space part of the suction
space 13 (Fig. 1 and Fig. 2) existing outside the suction-side shaft 2B of the male
rotor 2 collides against the side face of the working chamber closing unit 40, then
passes through the male-rotor-side open space 41A, flows within the suction space
13 and within the male-rotor-side open space 41A as if rotating around the suction-side
shaft 2B of the male rotor 2 in the same direction as the rotation direction of the
suction-side shaft 2B (the rotation direction indicated with arrow a), and is eventually
sucked into the working chamber through the suction port.
[0077] Similarly, with this screw compressor, the working medium which has flown through
the space part of the suction space 13 existing outside the suction-side shaft 3B
of the female rotor 3 collides against the side face of the working chamber closing
unit 40, then passes through the female-rotor-side open space 41B, flows within the
suction space 13 and within the female-rotor-side open space 41B as if rotating around
the suction-side shaft 3B of the female rotor 3 in the same direction as the rotation
direction of the suction-side shaft 3B (the rotation direction indicated with arrow
b), and is eventually sucked into the working chamber through the suction port.
[0078] The screw compressor according to this embodiment is configured as described above,
in a manner similar to that of the screw compressors according to the second and third
embodiments, so that the male-rotor-side open space 41A and the female-rotor-side
open space 41B are separated from each other; and, therefore, it exhibits the effect
of rectifying the working medium which flows within, for example, the suction space
13 along with the rotations of the male rotor 2 and the female rotor 3.
[0079] Consequently, if the screw compressor according to this embodiment is employed, the
working medium sucked through the suction opening 12 (Fig. 1) has lower flow resistance
than that of the conventional screw compressor and the suction of the working medium
into the working chamber is performed smoothly. Accordingly, when the male rotor 2
and the female rotor 3 rotate at a high speed, the speed is not decelerated when the
working medium flows into the working chamber; and, therefore, energy efficiency of
the screw compressor can be enhanced by suppressing the energy for accelerating the
working medium. Also, when the male rotor 2 and the female rotor 3 rotate at a low
speed, the flow rate of the working medium can be increased along with a reduction
of the suction resistance of the working medium.
[0080] In addition, with this screw compressor, a side-face shape of the male-rotor-side
recess 40A and a side-face shape of the female-rotor-side recess 40B of the working
chamber closing unit 40 are formed in a cylindrical shape whose curvature on the outlet
side of the male-rotor-side open space 41A or the female-rotor-side open space 41B
is larger than that on its inlet side in a manner similar to the third embodiment,
so that the speed of the working medium which flows out of the outlet side of the
male-rotor-side open space 41A or the female-rotor-side open space 41B to, for example,
the suction space 13 can be increased and the acceleration loss of the working medium
can be reduced.
[0081] Furthermore, with this screw compressor, the side-face shape of the male-rotor-side
recess 40A and the side-face shape of the female-rotor-side recess 40B are formed
in a substantially cylindrical shape, so that processing of the working chamber closing
unit 40 is facilitated, thereby making it possible to improve manufacturing efficiency
of the screw compressor and reduce manufacturing cost.
(5) Other Embodiments
[0082] Incidentally, the aforementioned first to fourth embodiments have described the case
where the present invention is applied to the screw compressor 1 in which the number
of lobes of the lobe unit 2A for the male rotor 2 is four and the number of lobes
of the lobe unit 3A for the female rotor 3 is six; however, the present invention
is not limited to this example and can be applied to a wide variety of screw compressors
with other various configurations.
[0083] Moreover, the aforementioned first to fourth embodiments have described the case
where each of the depressions 14C, 14D, 20D, 20E, 30D, 30E, 40A, 40B in the working
chamber closing member 14 or the working chamber closing units 20, 30, 40 is formed
in the arc shape which is coaxial with the male rotor 2 and the female rotor 3; however,
the present invention is not limited to this example and the above-described depression
14C, 14D, 20D, 20E, 30D, 30E, 40A, 40B may be of an arc shape which is not coaxial
with the male rotor 2 or the female rotor 3, or may be of any shape other than the
arc shape.
[0084] Furthermore, the aforementioned first embodiment has described the case where the
motor-side open space 15C is provided on the motor 9A side of the working chamber
closing member 14 and the male-rotor-side open space 15A and the female-rotor-side
open space 15B are provided on the side part of the working chamber closing member
14; and the second and third embodiments have described the case where the first and
second male-rotor-side open spaces 21A, 21B are provided on the male rotor 2 side
of the working chamber closing unit 20, 30 and the first and second female-rotor-side
open spaces 22A, 22B are provided on the female rotor 3 side of the working chamber
closing unit 20, 30. However, the present invention is not limited to this example
and, for example, in the first embodiment, the motor-side open space 15C and either
the rotor-side open space 15A or the female-rotor-side open space 15B may be provided;
and in the second and third embodiments, only the first male-rotor-side open space
21A and the first female-rotor-side open space 22A may be provided. Incidentally,
the case where only the second male-rotor-side open space 21B and the second female-rotor-side
open space 22B are provided in the second and third embodiments is the fourth embodiment.
INDUSTRIAL AVAILABILITY
[0085] The present invention can be applied to screw compressors with a wide variety of
configurations.
REFERENCE SIGNS LIST
[0086]
1: screw compressor
2: male rotor
2A, 3A: lobe unit
2B, 3B: suction-side shaft
2C, 3C: delivery-side shaft
3: female rotor
4: casing
9: drive unit
9A: motor
10, 10X to 10Z: main casing
10A, 10AX to 10AZ: bore
12: suction opening
13: suction space
14: working chamber closing member
14C, 14D, 20D, 20E, 30D, 30E, 40A, 40B: depression
15, 21, 22, 31, 32: open space
15A, 21A, 21B, 31A, 31B, 41A: male-rotor-side open space
15B, 22A, 22B, 32A, 32B, 41B: female-rotor-side open space
15C: motor-side open space
20, 30, 40: working chamber closing unit
20A, 30A: male-rotor-side recess
20B, 30B: female-rotor-side recess
20C: isolation wall